Continuous winding machine



P 94 I w. s. ORBlN EI'AL 2,385,691

CONTINUOUS WINDING MACHINE Filed March 12, 1942 l4 Sheets-Sheet 1 W. s. CORBIN ETAL 2,385,691

commuous WINDING mcumm Sept. 25, 1945.

Filed March 12, 1942 14 Sheets-Sheet 2 p 1945. w. s. CORBIN ETAL CONTINUOUS WINDING MACHINE 14 Sheet-S -Sheet 3 Filed March 12, 1942 Sept. 25, 1945.

W. S. CORBIN ETAL CONTINUOUS WINDING MACHINE 14 Sheets-Sheet 4 Filed March 12, 1942 Sept. 25, 1945. w. s. CORBIN ET AL 2,385,691

CONTINUOUS WINDING MACHINE Filed March 12 1942 14 Sheets-Sheet 5 P 1945. w. s. CORBIN ETAL 2,385,691

CONTINUOUS WINDING MACHINE Filed March 12, 1942 14 SheetsSheet 6 #5 I I r /09 5/ Sept. 25, 1945. w. s. CORBIN EI'AL CONTINUOUS WINDING MACHINE m& 7 w WWW w. w w m i l Maw m .11 a e F W i. 4

ifas/ 170' Filed March 12, 1942 1 Sept. 25, 1945. w. s. CORBIN ETAL CONTINUOUS WINDING MACHINE l4 Sheets-Sheet 8 Filed March 12, 1942 lllll Sept. 25, 1945. w. s. CORBIN EI'AL CONTINUOUS WINDING MACHINE Filed March 12, 1942 14 Sheets-Sheet 9 HHHHHHHHH HH L. llllllll l I .F llll I I Dept. 25, 1945. w. s. CORBIN ETAL CONTINUOUS WINDING MACHINE Filed March 12, 1942 14 Sheets-Sheet 10 Q Q Q Q QQ Q P 1945- w. s. CORBIN ETAL 2,385,691

CONTINUOUS WINDING MACHINE Filed March 12, 1942 14 Sheets-Sheet 11 I P 25, 1945. w. s. CORBIN ETAL 2,385,691

CONTINUOUS WINDING MACHINE Filed March 12, 1942 14 Sheets-Sheet 12 14 Sheets-Sheet 15 W. S. CORBIN ETAL CONTINUOUS WINDING MACHINE Filed March 12, 1942 Sept. 25, 1945.

P 1945. w. s. CORBIN ETAL 2,385,691

CONTINUOUS WINDING MACHINE Filed March 12, 1942 14 Sheets-Sheet 14 Patented Sept. 25, 1945 UNITED STATES CONTINUOUS WINDING MACHINE Wesley 8. Corbin, Bldley Park, Pa., Francis Chil- 5011 Plainflcld, N. ington,

e, N. Y., Paul L. Tollison, North 1., Charles S. Cailrey, Port Wash- N. Y., and Alfred F. Pilon, North Plainileld, N. 1., asslgnors to Scott Paper Company, Chester, Pa., a corporation of Pennsylvania Application March 12, 1942, Serial No. 434,430

42 Claims.

I to provide a machine of the stated type which will operate continuously, and without interruption i'orthe necessary transfer operations, at, a constant and materially higher rate of speed than has heretofore been found practicable in machines of this class, particularly in the processing of tissue and similar papers.

The invention provides improved transfer, winding, and control mechanisms all contributing to the desired primary ends of increased production capacity, improved functional efllciency, elimination of waste both in time and product, and the production of high quality rolls of predetermined diametrical size.

In the attached drawings;

Figure 1 is a side elevational and partial sectional view of a machine made in accordance with the invention;

Fig. 1a is a diagrammatic side elevational vie showing the parent roll driving means;

Fig. 2 is a vertical sectional view, in diagram,

of the upper portion of the machine;

Fig. 3 is a fragmentary view in perspective of elements of the perforating mechanism;

Figs. 4 and 4a are fragmentary views in front elevation of one side of the machine showing detail of the transmission mechanism;

Fig. 5 is a sectional view on the line 55, Fig. 4a;

Fig. 6 is a sectional view on the line 8-4, 18. 5;

Fig. 7 is a sectional view on the line 1-1, Fig. 5;

Fig. 8 is a fragmentary sectional view, but on a reduced scale, corresponding to Fig. 5, and. with the latter illustrates a phase of themechanical operation of the machine;

Fig. 9 is a view. in front elevation ofthe opposite side of the machine from that shown in Fig. 4;

Fig. 12 is a side elevational view of the part of the machine shown in Fig. 9;

Fig. 13 is a sectional view on the line "-43, Fig. 9; r c Fig. 14 is a view in rear elevation of the same side of the machine shown in Fig. 9;

Fig. 15 is a vertical axial sectional view of that portion of the reel shown in Fig. 14;

Fig. 16 is a view in perspective of one of the 10 elements of reel clutch mechanism:

Fig. 1'1 is a sectional view on the line l'I-ll, Fig. 1;

Fig. 18 is a sectional view on the line ll-ll, Fig. 1; I l Fig. 19 is a fragmentary sectional perspective view showing details of the reel assembly;

Figs. 20 and 21 are views in perspective of elements of the reel assembly;

Fig. 22 is a longitudinal sectional view of the 2 drum;

Fig. 23 is a sectional view on-the line 23-23, Fig. 24; Fig. 24 is a sectional view on the line 24-24, Fig. 23: 7 Fig. 25 presents views in perspective of one of the elements of the air valve; Fig. 26 is a section on the line 26-46, Fig. 17; Fig. 2'7 is a view in perspective of one of the core-grippin fingers of the reel;

Fig. 12;'

Fig. 29 is a diagrammatic view of one of the safety devices with which the machine is provided; Figs. 30 to 33, inclusive, are fragmentary sectional and side elevational views illustrating the details and mode of operation of the transfer in contact with the drum is wound upon a core 6 so as to produce a roll I, see Fig. 2, of relatively small predetermined diameter and paper content.

As the roll I is completed, an additional core, ad'- vancing on a rotary reel 8, moves into position to receive the web I, and the web is then transferred to this core for a repetition of the winding operation. The reel 8 receives the additional cores from a hopper II- and carries them successively to the drum, and the transfer operations Fig. 28 is a sectional view on the line 28-28,

roll 2, passes to a rotary drum 3, and while still are effected without interruption of the movement of the web, so that the operation of the machine is continuous.

This reel also carries position to continue the winding operation; and means, forming no part of the present invention, and including an autopaster I3, is provided for automatically joining the inner terminal end of the one roll to the outer end of the succeeding roll so that the winding operation may be 'con-, tinuous and without interruption. The parent roll is driven during the winding operation through the medium of a belt or belts I4. This belt is driven through a variable speed drive unit I6 of commercial type. the unitpreferably being operatively connected through a sprocket I6 and chain I1 directly with the trunnion 33 of the drum 3, or directly with the motor (not shown) which operates the drum. The unit I5 is operatively connected through suitable transmission gearing, including sprockets I9 an 2| and a chain 22, with a drive pulley 23 for the belt I4. The belt I4, as. illustrated, bears against the master roll 2 on the reel I2; and means is provided at 24 for tensioning the belt with respect both to the drive pulley 23 and the master roll 2. The ratio of the input and output speeds of the unit. I5 is controlled by the movement of a tension roll 26 which engages the web I as shown and which is operatively connected with the variable speed unit I5, preferably by hydraulic means not shown and forming no part of the present invention, so as to regulate the speed of the belt I4, and by the effect of this regulation on the parent roll 2 to obtain and to maintain a predetermined tension in the web.- With the arrangement shown, the linear speed of the web I is not affected by the changing diameter of the parent roll, so that the tension tends to remain constant. e In passing to the drum 3, the web I engages a roll 21, this roll having in its surface a spiral fluting or'the like extending in opposite directions from the center of the roll and functioning in known manner to smooth the web I preparatory to its engagement with the drum 3. Preferably this roll is driven in the direction of the web, as indicated by the arrow in Fig. 2, and at a peripheral speed slightly greater than the linear through the medium of a rotary perforating head 28 having secured in and projecting from the periphery thereof a uniformly spaced series of perforating blades 23. The blades 29 are of a character to perforate the roll without severing the web. The head 28 is rotated in synchronism with the drum 3, and the surface of the latter is provided with a series of uniformly spaced axially extending slots or recesses 3| for recep-. tion of the projecting edges of the said blades.

Since the tensioned web I overlies the slotted recesses 3|, the blades 29 in entering the recesses perforate the web in well known manner.

It is to be noted by reference to Fig. 1 that the rolls 4 and 6 and the head 28 each receives its rotary movement from a gear wheel 32 carried by the trunnion 33 of the drum 3. Attached to an end of each of the rolls 4 and 6 is a gear 34 which meshes with the ar 32 as shown, and the head 28 carries at one end a gear 35 which similarly meshes with the gear 32. The peripheral speed -of the head 23 is the same as the speed of the drum 3, but the peripheral speed of the roll 4 is preferably somewhat slower than the peripheral speed ofthe drum 3 so as to afford a slight dragging action on the web as it passes to the perforating position and to thereby offset the tendency of the blades 23, which by reason of their projection beyond the surface of the head 28 will have .a linear speed somewhat greater than the linear speed of the web, to drag the web forward into the recesses 3I in the drum. Preferably the roll 4 is located as close as possible to the head 23 so as to reduce to a minimum the length of web extending between the bite of the roll 4 and the point of perforation. Correspondingly the surface speed of the roll 6 is somewhat greater than the peripheral speed of the drum, so that this roll tends to draw the paper web firmly across the slot during the perforating operation.

The rolls 4 and 5 are not tight against the paper, and will not, in spite of the fact that their surface speeds differ from the surface speed of the drum, affect the speed of the web with the drum speed. As shown in Fig. 1, the position of the rolls 4 and 6 with respect to the surface of the drum 3 may be regulated by means of an adjusting screw 36, one of these screws being threaded into each of the journals 31 of the rolls,

and the journals being slidably mounted in the frame. The screw 36 passes freely through an element 33 which is secured to the frame and forms a seat for a spring 39, said spring exerting pressure on the adjustable journal element 31 to resiliently hold the roll in an advanced position. The head of the screw 36 bears against a clamping collar H which seats upon the member 33 and is prevented from turning on said member by a pin 42 which extends from the clamp into an aper-.

ture in said member. When the clamping collar 4| is tightened, through the medium of a screw 43, upon the bolt, the latter is held rigidly in adjusted position, and in this position acts as a stop to limit the advance movement of the journal 31 under the pressure of the spring 39.

A safety device is associated with the screw 36, said device'taking the form in the present instance of a micro switch 44 having an actuator 45 engaging the clamping collar 4I. Any outward movement of the roll 5 from the roll 3 causes a movement of .the actuator 45, and the latter is adjusted so that ifthe outward movement of the roll 5 from the drum 3 is abnormal, the switch will be actuated. As shown in Fig. 29, this switch is connected in a circuit which includes a solenoid 46. When the switch, which is normally open, is closed by abnormal movement of the roll 5 away from the roll 3, the solenoid 46 will be energized. The solenoid is connected to a cutter blade 41, which as shown in Fig. 1 lies across the path of the web I, said blade being normally held in a retracted position by action of a spring 48. Energization of the solenoid 46, acting through inclined slots 49, 49, and relatively fixed pins 5|, causes the blade to move downwardly, and in this downward movement to coact with a relatively fixed blade 52 at the under side of the web to shear the latter. The roll 4 is provided with a similar adjusting means and safety switch 53-54, and as shown in Fig. 29, this switch also is connected in the circuit of the solenoid 46 so that when the switch is closed by excessive movement of the roll I away from the drum 3, the blade 41 will be actuated to sever-the web as desired above.

From the roll the web I passes around-the drum 3 to a position at the top of the latter where it is started around one of the cores 6 which, as previously described, has been brought into position for this operation by the reel 8. The reel carries a uniformly spaced series of rolls 55 of special form hereinafter described, and between each pair of these rolls is mounted a coregripping device, designated generally by the reference numeral 56, which devices receive the cores 6 from the hopper H and hold them immovably until the reel has turned sufficiently to bring the core into position adjoining the top of the drum 3.

The framework of the reel itself is composed of two heads, 5! and 58, which are keyed to opposite ends of the shaft it, said heads being rigid- 1y connected by an annular series of rectangular bars 59. Each of the heads El and 58 has a IKE- ripheral recess 6%, and mounted within this recess and between abutments 62 is aseries of members 63 which are slidable in radial direction and which constitute the supports for the core-gripping elements. These elements, one of which is shown detached in Fig, 2'7, comprises a tail portion 6 and a laterally offset segmental gripping portion 65. The tail portion M of the element, as shown in Figs. 26 and 17, is pivotally mounted in slots 66 of the members 63 upon pivot pins 6?, and normally a spring 68 draws the two gripping portions 65 of each pair together in mutual core-gripping position. Sliding movement of each of the members 63 is eifected through the medium of a roller 69 on the outer end thereof, which roller engages the surface of a cam M. This cam partially embraces the end of the reel, as best shown in Fig. 2, and acts through the roller 69 during part of the rotation of the reel to maintain the members 63 in a retracted po-.

sition against the pressure of a spring 12 which engages the inner end of each of the slides, as shown in Fig. 26. 7 When the members 63 are thus retracted, the tail portions 64 of each of the coacting pairs of core-gripping elements are forced towards each other by relatively fixed rollers 13, these rollers being loosely supported on rock shafts 14 which extend between and are journaled in the heads 51 and 58.

Referring again to Fig. 2, it will be noted that the cams H at the respective ends of the reel extend from a point adjacent the hopper ll around the reel in a direction counter to the direction of rotation of the latter and beyond the point where the reel most closely adjoins the drum 3. As each of the rollers 69 passes under the discharge end of the hopper II, it is still in engagement with the cam II, and the gripping elements 65 are, therefore, separated as illustrated. These elements are then in position to receive the opposite ends of one of the cores 6, which by suitable mechanism, such, for example, as illustrated at 1.5 in Fig. 2, is allowed to drop from the hopper. The roller 69 now passes out of engagement with the cam H, the member 63 slides upwardly under action of the spring 12, and the gripping elements 65 come together on opposite sides of the core. The core is thus clamped immovably in the reel until the roller 69 again passes into engagement with the cam H, at which time the supporting member 63 is radially retracted and the rollers 1: separate the gripping elements to release the core. which then finds support throughout its length upon the drum 3 and the paper web I which at that point overlies the drum surface.

It is to be noted that by reasonof the positions of the core-gripping devices 56 between the,

spaced rolls 55 and by reason of the relative positions of these rolls on the reel 'and with respect to the surface of the drum 3, the cores 6 when released from the clamps 65 are caged between the drum 3 on the one hand, and the contiguous pair of rolls 55 on the other hand, as shown in Figs. 2 and 26. The core is now in position to receive the web I for the winding operation.

In describing this phase of the machine and its operation, it will be assumed that one of the rewound rolls I has been carried to the point of completion, as shown, for example, in Fig. 2. The succeeding core 6 is now in position to receive the web as described above, and as also shown in Fig. 2. The operation whereby the web is transferred to the new core is effected, in a preferred embodiment of the invention. in the manner best illustrated in Figs. 2, 26, and, 31 to 33, inclusive. The desired result is effected by means of compressed air operating through suitable devices in the drum 3 to elevate the web from the surface of the drum, so that the latter while still intact is caught in the nip between the core and one of the caging roll 55.

As illustrated, the drum 3 is formed so as to provide in the interior thereof a chamber 16 for compressed air, the said air being admitted to this chamber from a suitable external source through a hollow trunnion H, as shown inFig. 22. .The chamber 16 communicates through ports 18 with a valve chamber 19 whichextends longitudinally of the drum and which is provided with a discharge port in the form of a, longitudinally extending slot 8| opening to the periphery of the drum as illustrated. A valve device 82 is mounted in the chamber 19 and controls the passage of air to the slotted discharge nozzle 8|. As shown in the drawings, the nozzles 8| are somewhat inclined to a radial plane of the drum in reverse direction to the rotation of the drum. Normally the outer end of the nozzle 8| will be covered by the paper web I, and the nozzle is so located with respect to one of the perforating slots 3| that the nozzle will underlie the web on a transverse line intermediate two of the rows of perforations.

In Fig. 30, we have illustrated the various parts approximately in the position at which the transfer operation is initiated by'the opening of the valve 82 to admit compressed air to the nozzle parts 8i. In Fig. 26, 'we have illustrated an early effect of the air upon the traveling web I, it being noted that above the slot 8|, the web I has been elevated from the surface of the drum 3 and against the surface of the core 6 which now is confined by the contiguous pair of caging rolls 55. The core 6, when released from the reel clamps 65, is immediately set in rotation by engagement with the traveling web, and since the rolls55 are driven at a peripheral speed slightly greater than the linear speed of the web, the core at the moment of transfer has a peripheral speed at least as great as the linear speed of the web. A the movement continues, with the air still discharging from the nozzle BI and as shown in Fig. 32, the web is still further elevated in the form of a loop against the face of the core 6 and toward the nip between the rota-t ing core and the leading one of the casing rolls 55. In Fig. 31, the loop in the web caused by the action of the compressed aIr as described above has been carried into the nip between the roll and the core, with the result, also as shown in Fig. 31, that the web is pulled apart and ruptured along one of the transverse lines of perforation between the now completed roll 1 and the new core 8. The free end of the web is now carried completely around the rotating core 8, as shown in Fig. 33, and the transfer is thereby completed with the initiation of the rewinding operation on the new core. The loop formed by the action of the air and which is forced by the latter into the nip of the core and caging roll, as described, results in part from a stretching of the web and in part by slack drawn largely from the portion of the web passing to the preceding roll. The loop is uniform throughout the width of the web, and the rupture of the web resulting from the engagement of the loop in the nip of the core and caging roll takes place accurately along one of the lines of perforations.

Means is provided on the reel for directing the air and for guiding the free end of the web around the core 8, this device being shown in Figs. 19 to 21, inclusive. As therein shown, the surfaces of the rolls 55 are, in effect, interrupted longitudinally by circumferential recesses 83. Secured to the rods 58 and extending outwardly between the respective adjoining pairs of the rolls 55 and into the recesses 83 of one of the rolls of said pair are guide shoes 84, one of these shoes being shown detached in Fig. 21. As shown in Fig. 31, these shoes 84 partially embrace that side of the new core 8 over which the web is initially passed and extend into the recesses 83 of that one of the rolls 55 which coacts with the core to nip the loop in the web caused b the compressed air, as previously described. Each of the shoes 84 is provided with a transverse opening 85 for reception of a rod 88 which extends continuously through the apertures of all of the shoes 84 of each longitudinal series. This rod 88 forms a pivot for a second set of shoe 81 which extend oppositely to the shoes 84 and into the recesses 83 of the opposite caging roll 55.. One of the shoes 81'is provided for each of the said recesses 83. These shoes 81 more closely embrace the side of the core 6, as shown in Fig. 31, so as to effectively direct the free end of the web as it passes around the core into the nip between the core and underlying drum 3. Secured to the under sides of the shoes 84 and bridging the juncture between the shoes 84 and 81 is-a curved plate 88, this plate extending continuously throughout the entire longitudinal series of shoes 84 and 81 and throughout the length of the associated rolls 55. As best shown in Fig. 31, the longitudinal edges of these plates 88 are in contact with. the surfaces of the two opposed rolls 55, 55, and the said longitudinal edges are beveled, as indicated at 89, so as to permit them to function after the manner of a doctor blade and with respect to the surfaces of the rolls 55, 55 to preclude possibility of any portion of the web adhering to the surfaces of the rolls and to insure a properdirection of the free end. of the web around the surface of the core 8. The relation of the various parts described abo e is well shown in Fig. 31.

The shoes 84 fit neatly between the sides of the respective recesses 83 so that they form with the intervening portions of the roll 55 what in effect is a substantially solid baille extending from the outer extremities of the shoes to the proximate longitudinal edge of the bridge plate 88. This plate forms a continuation of the battle between the cooperating cage rolls. The shoes 81, unlike the shoes 84, are formed with openings 98 so that in this case the effect of the solid baiile is lost. Thus, while the solid baflle at the one side and at the top of the core 8 directs the stream of air, and also guides the web, into the bite of the near roll and the core and over the top of the latter, the shoes 81 permit the air to escape freely at the other side of the core and function primarily as guides to direct the free end of the web into the bite of the core with the drum. This release of the air above the ends of the shoes 81 is necessary inorder to maintain a free and unobstructed flow of air upwardly and over the core from the other side and to prevent the air by reaction with the drum from interfering with the smooth passage of the free end of the web be tween the core and the drum.

Since the winding operation takes place durin the continued rotary movement of the reel and while the roll is caged between the rolls 55 of the reel and the drum 3, it is necessary to provide means for retracting the guide shoes 81 so as to avoid contact between the outer ends of the shoes and the growing roll. This retraction of the shoes 81 is effected through the medium of the rock shafts 14 to which the shoes 81 of each longitudinal series are operatively connected by links 8|. As shown in Fi 15, the end of each of the rock shafts 14 is provided with an arm 92, and on the arm with a roller 83 which operatively engages a relatively fixed cam 94. As the reel rotates, this cam operates through the arm 82 to rock the shaft 14 and to thereby advance and retract the guide shoe 81, the advanced position being occupied by the shoe during the transfer period.

The valve device which controls the air port 8| is best illustrated in Figs. 22 to 26, inclusive. The device comprises two housing members and 88 which are set into the drum 3 as illustrated, the outer longitudinal face of the member 85 forming a part of the cylindrical face of the drum. The cylindrical valve member 82 seats accurately within a semi-cylindrical socket which extends longitudinally of the inner face of the housing member 85. Loosely seated in a longitudinal recess 81 of the member 82 is a series of segmental valve elements 88, one of these elements being shown detached in Fig. 25. These elements 88 which extend in unbroken series longitudinally of the member 82 overlie a longitudinal slot 88, and from the bottom of this slot a plurality of ports |8| extend to the opposite side of the member .82. Each of the elements 88 has a longitudinal series of apertures I82, and the outer ends of these apertures are arranged to coincide with the inner ends of a correspond-- ing number of ports I83 which extend from the aforesaid semi-cylindrical seat in the member 85 to the inner end of the slot 8|.

when the member 82 is in the position shown in Fig. 26, air passes freely from the chamber 18 through the ports 18, the chamber 18, the ports I8I, and the ports I82 to the apertures I83, and thence to and through the slot 8|. It will be noted that the apertures I83 are closely set so that the. flow of air to and through the slot 8| will be substantially uniform from end to end. When the member 82 is shifted, as hereinafter described, to the position shown in Fig. 24, the inner ends of the apertures I83 will be covered by the side portions of the series of segmental valve elements 98. Since these elements are loose in the member 82, the compressed air will act to force them tightly against the cylindrical seat I 00, with the result that the inner ends of the ports I03 will be sealed. It is to be noted that the elements 98 are carefully formed so that their surfaces conform accurately to the curved surface of the seat I00, and it will be noted further that the junctures between the ends of the adjoining elements 96 lie in each case intermediate two of the openings I03. The angular arrangement of the slot 8|, which was previously mentioned and which is clearly shown in the drawings, has the effect of aiding in the operation of forcing the web upwardly around the new core in the transfer operation, as well illustrated in Fig. 26, and since the slot BI is also angularly disposed with respect to the longitudinal axes of the ports I03, the air projected through the latter into the slot and striking the inclined side of the latter has a tendency to spread transversely and to thereby more uniformly distribute itself throughout the slot.

The member 82 is journaled in bearings I04 in the ends of the housing members 95 and 96, as illustrated in Fig. 23, and the joint between the journaled portions of the member 82 is sealed by means of packing glands I which are flanged,

as shown in Figs. 4a and 8, and are secured to the ends of the housing sections 95 and 96 by means of screws I06. The mid portion of the valve member 82 is supported by a block I01, as shown in Fi 23.

The manner in which the member 82 is actuated to open and close the air discharge ports is illustrated in Figs. 5 to 8, inclusive, and Fig. 44a. To each end of the member 82 is secured an arm I08, and the outer end of each of these arms is connected by a rod I09 to a link III, which link is pivotally connected at II2 to the end of the drum 3. The rod I09 passes through an aperture H3 in the end portion I I4 of thedrum 3. One end of this aperture H3 is countersunk, as shown in dotted lines in Fig. 2, for reception of a spring II5 which embraces the rod I09 and which exerts resilient pressure tending to hold the parts in a position in which the valve is closed, as illustrated in Fig. 24. At the' outer end of the link II I is a roller I I6 which is adapted for engagement with a cam element I I1 pivotally supported at I I8 in the fixed structure of the machine. When this cam element H1 is depressed, as shown in full lines in Fig. 5, it is inoperative with respect to the roller II6, but when elevated, as shown in broken lines, it lies in the path of the roller H6, and when engaged by the latter will act to shift the rod I09 longitudinally and thereby oscillate the member 82 to bring thevalve to the open position, see Fig. 2. A rock shaft I I9 extends transversely of the machine and has at each end an arm I2I positioned for engagement with the under side of the cam II1. It will be understood that insofar as described, the actuating means for the member 82 is duplicated at opposite sides of the machine and for opposite ends of the said member.

The rock shaft I I9 is actuated through the medium of a pair of cams I22 and I23. The peripheral edges of these cams form a common support for a lever arm I24 which is pivotally secured at.

I25 to the fixed structure of. the machine and which has attached to its outer end a link I26 which connects the'said lever to an arm I21 on the shaft I I9. A spring I28 normally exerts force tending to hold the link I26 in a depressed position wherein a pair of cam rollers I29 and I3I carried by the lever I24 are engaged with the peripheral surfaces of the respective cams I22 and I23. The cam I22 has a peripheral recess I32, and a corresponding recess I33 is provided in the cam I23. The rollers I29 and I3I are mounted on a common axis, and when, therefore, and only when, the two recesses I32 and I33 are in axial alignment, the rollers I29 and I3I will be permitted to move downwardly into the said recesses to thereby depress the outer end of the lever 24, and to rock the shaft H9 in a direction causing the arms I2I to elevate the cams H1.

The cam I23 is secured to a shaft I34, and this shaft is driven from a shaft I35 through the medium of a worm I36 on the latter and a worm wheel I31 on the shaft I34. The shaft I34 carries a gear I38 which meshes with a gear I39 on a stub shaft I4I, this shaft also having secured thereto a second gear I42. This latter gear meshes with a gear I43 which is journaled 0n the shaft I34 for movement with respect to the latter, and the cam I22 is secured to the gear I43 by means of screws I44, see Fig. '1. It will be apparent that through this transmission device the cams I22 and I23 will be driven at different speeds, and one at a considerably faster rate than the other. This device affords a relatively rapid actuation of the parts and a desirable quick opening and closing of the valve.

The drum 8 is continuously rotated from a drive shaft I45, (which is connected to a suitable source of power, not shown), through the medium of gears I46, I41 and I48, the latter meshin with the gear 32 on the drum trunnion 33. The reel 8, on the other hand, has an intermittent rotation and is held stationary and locked in position during the transfer operations described above. The reel is actuated through a reciprocatory rack I49 slidably supported in the fixed framework of the machine and a pinion I5I on the reel shaft I8, see Figs. 9 to 14, inclusive. Re-

'ciprocation of the rack I49 is effected through a cam I52 which engages a roller I53 on an offset extension I54 of the rack. As illustrated in Figs. 12 and 14, the cam I52 is carried on a stub shaft I55, the outer end of which is journaled in a bracket I56 secured to the main frame I51 of the machine. The inner end of the shaft is provided with a bevel gear I58 which is connected to the power source, as hereinafter set forth. The extension I54 of the'rack I49 has attached thereto a spring I59, andthe other end of this spring is attached at I6I to the upper cross member I62 of the bracket I56. This spring exerts a continuous force tending to move the rack upwardly, as viewed in Fig. 12, and thereby maintains the roller I53 in engagement with the periphery of the actuating cam I52. It will b noted from Figs. 12 and 14 that the lower portion of the rack extension I54 is provided with a slotted opening I83 which embraces the shaft I55 and thus helps to support and guide the extension I54 in its longitudinal reciprocatory movement.

The toothed pinion I5I which engages the rack I 49 is loosely mounted upon a sleeve I64, which sleeve is keyed to the shaft I8, all as shown in Fig. 10. The sleeve I64 has at its inner end a flange I65, the peripheral surface of which is provided with a plurality of radially extending recesses I66 arranged in uniformly spaced series around the said periphery. The outer axial face of the flange I65 is provided with an annular series of projecting lugs I61, and the adjoining face of the pinion II has a corresponding series of lugs I68 which are adapted to mesh with the lugs I61 to thereby interlock the pinion I5I with the sleeve I64, and through the sleeve with the shaft I8. The lugs I61 and I68 constitute in effect the interengaging elements of a dog clutch by means of which the sleeve and pinion may be operatively connected. When the pinion I5I is shifted from the position in which it is shown in Fig. 10, the .elements I61 and I68 will become disengaged, thereby freeing the pinion I5I from the shaft I8 and permitting its free rotation on the outer end of the sleeve I64 as a journal.

Means is provided for engaging and disengaging the pinion I5I with and from the sleeve I64. This means comprises a bifurcated lever I69 carrying shoes I1I which engage respectively in opposite sides of a circumferential recess I12 in the pinion I5I. The lever I69 is pivotally connected at I13 to the fixed structure of the machine and has a transversely extending arm I14 to which is connected a spring I15, this spring exerting continuous force tending to shift the lever on its pivot I13 in a direction to move the pinion I5I to the outer end of the sleeve I64, in which position, as set forth above, it is disengaged from the clutch elements I61 of the sleeve. The lever I69 extends below the pivot I13, and at its lower end carries a cam roller I16 which engages the face of a cam element I11. This element is slidably supported in the frame of the machine and is connected through a rod I18 with a bell crank lever I19, said lever being pivotally supported at I8I on the cross piece I62 of the bracket I56. The other end of the bell crank lever I19 carries a roller I82 which engages a cam I83 secured to the shaft I55, the contour of this cam being shown in broken lines in Fig. 12. A spring I84 on the rod I18 tends to retain the rod in an elevated position, and to maintain the roller I82 in engagement with the cam I83. Elevation of the cam I11 by action of the cam I83 has the effect of shifting the pinion I 5| to the left, as viewed in Figs. '9 and 10, against the action of the spring I15, and to thereby engage the clutch elements I68 of the pinion with the corresponding elements I61 on the sleeve I64. When i the cam I11 is moved to its alternate low position, the spring I15 operates to disengage the clutch elements.

In these movements of the pinion I5 I the teeth thereof remain continuously in mesh with the teeth of the rack I49. The cams I52 and I83 are so related that while the former is operating to move the rack I49 downwardly, the pinion I5I is interlocked with the sleeve I64, and therethrough with the shaft I8 whereby the reel 8 is rotated in the required direction. At the lower end of the downward movement of the rack I49, the cam I83 operates to disengage the pinion I5I from the sleeve I65 and the shaft I8, and the pinion I5I is thereby free to rotate on the sleeve without affecting the position of the reel 8 during the upward stroke of the rack. At the upper end of the rack movement, the cam I83 again acts to engage the pinion with the shaft I8, so that the subsequent downward movement of the rack causes a further rotational movement of the reel.

Means is also provided for positively locking the reel in place during the periods in which the rack is inoperative with respect thereto. Slidably mounted in the frame is a latch member I85, and this latch is adapted to engage in one or other of the recesses I66 in the periphery of the sleeve I64 to thereby lock the sleeve and with it the reel shaft I8 in fixed position. This function of the latch I is illustrated in Fig. 10. A spring I86 tends to force the latch into the elevated or operative position. A lever I81 is pivotally secured in the frame by a pin I88, and the inner end of this lever is slotted for reception of a pin I89 on the latch element I65. Pivotally connected by means of a pin I 9I to the outer end of the lever I81 is a block I92 which seats upon a projecting arm I93 of the cam element I11. When this cam element is depressed, therefore, as previously described, so as to permit the spring I16 to release the pinion I5I from its clutching engagement with the sleeve I64, the outer end of the lever I81 is permitted to move downwardly so'that the spring I86 is operative to elevate the latch element I85 into meet the recesses I66 in the sleeve I64, as shown in Fig. 18. Elevation of the cam element I 11 to reengage the pinion I5I with the sleeve I64 causes an elevation of the outer end of the lever I81 and a consequent downward retraction of the latch I85 from the recess I66 in the sleeve. It will be noted that the recesses I66 of the sleeve. I65 and the latch I85 are arranged so that when the reel is locked in position by operation of this device, one or other of the core-retaining elements of the reel will be in proper position with respect to the drum 3 for the transfer of the web to a new core, as described above.

As previously set forth, the caging rolls 65 of the reel are driven so that their peripheral speeds are slightly greater than the peripheral speed of the drum 3. As shown in Figs. 17 and 18, each of the rolls 55 is journaled at I94 in the head mem bers 51 of the reel, and each of the rolls has at its extremity a pinion I95. All of the pinions I85 mesh with one element I96 of a composite gear I98 which is journaled freely on the shaft I8. The other element I91 of this composite gear meshes with a pinion I98 at one end of a stub shaft I99 journaled in the fixed frame of the machine, and the other end of this shaft carries a pinion 28I which is connected through an idler gear 282 with the gear 32 of the drum 3. The

rolls 55 are thus driven from the same source of power which operates the drum 3.

' The shaft I55 which carries the cams I52 and I83 previously described receives its motion from a shaft 283. A bevel pinion 284 on this shaft meshes with the bevel gear I58 on the shaft I55. The shaft 283 is driven in turn from the drum 3 through the medium of a gear train best shown in Figs. 9 and 12. The drum trunnion 33 has loosely mounted thereon a gear 285, and this gear is normally locked with the shaft by means of a latching device shown in Figs. 13 and 28. This device comprises a latch 286 which is slidably supported in a sleeve 281 secured to the end of the shaft 33 and on which the gear 285 is journaled, said latch passing into an apertured lug 288 on the gear 285. A spring 289 tends to hold the latch in the advanced or operative position, as shown in Fig. 13, and the latch may be retracted through a handle element 2I I to release the gear 285 from the shaft.

The gear 285 is sufllciently broad of face to engage two gears 2 I2 and 2 I3, which are of dilferent pitch diameters and are journaled upon relatively eccentric journals 2 and 2I6 on a common stub shaft secured to the fixed framework of the machine, see Fig. 28. The gears 2I2 and 2I3 are adapted to mesh respectively with separate gear elements 2I6 and 2" of a composite gear 2I8 which is splined to a shaft 2| 8 loumaled in the 

